JP3919366B2 - Shell-type needle roller bearings for universal joints for steering - Google Patents

Shell-type needle roller bearings for universal joints for steering Download PDF

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Publication number
JP3919366B2
JP3919366B2 JP34638598A JP34638598A JP3919366B2 JP 3919366 B2 JP3919366 B2 JP 3919366B2 JP 34638598 A JP34638598 A JP 34638598A JP 34638598 A JP34638598 A JP 34638598A JP 3919366 B2 JP3919366 B2 JP 3919366B2
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Japan
Prior art keywords
needle roller
shell
cylindrical portion
outer ring
bearing
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Expired - Fee Related
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JP34638598A
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Japanese (ja)
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JP2000170755A (en
Inventor
一由 針本
信吾 河野
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NTN Corp
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NTN Corp
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Priority to JP34638598A priority Critical patent/JP3919366B2/en
Priority to DE19958059A priority patent/DE19958059A1/en
Priority to US09/453,212 priority patent/US6334714B1/en
Publication of JP2000170755A publication Critical patent/JP2000170755A/en
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Publication of JP3919366B2 publication Critical patent/JP3919366B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
    • F16D3/385—Bearing cup; Bearing construction; Bearing seal; Mounting of bearing on the intermediate member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/588—Races of sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings

Description

【０００１】
【発明の属する技術分野】
この発明は、自在継手に組込まれる針状ころ軸受に関するものである。
【０００２】
【従来の技術】
ステアリングホイールの回転によって車輪を操舵する自動車のステアリング装置には、ステアリングホイールの回転をステアリングギアボックスに伝えるステアリングシャフトを相対的に角度をもつ２軸で形成し、その２軸を自在継手で連結して、２軸の相互間で回転トルクを伝えるようにしたものが知られている。
【０００３】
図３（Ｉ）、（II）は、上記ステアリング装置に用いられる自在継手の一例を示す。この自在継手は、一対のヨーク２０のそれぞれに設けられた二股片２１に軸受孔２２を形成し、各軸受孔２２にスパイダ２３に設けられたトラニオン２４を挿入し、各トラニオン２４を軸受孔２２に圧入されたシエル形針状ころ軸受３０で回転自在に支持している。
【０００４】
ここで、シエル形針状ころ軸受３０は、軸受孔２２内に圧入される円筒部３１ａの一端に底３１ｂを設けた外輪３１と、上記円筒部３１ａの内周の軌道面３２に沿って転動自在の複数の針状ころ３３とから成り、前記外輪３１は金属薄板のプレス成形品とされている。
【０００５】
上記の構成から成る自在継手において、スパイダ２３のトラニオン２４と針状ころ軸受３０との間にラジアルすきま△ｒがあると、一対のヨーク２０の接続部間にラジアルすきま分に相当するガタつきが生じ、各ヨーク２０に接続される２軸の相互間で円滑に回転トルクを伝達することができなくなる。
【０００６】
このため、ステアリング装置においては、ステアリングホイールの回転操作性の向上を図るため、針状ころ軸受とトラニオンの相互間におけるラジアルすきまの狭小化が要望されている。
【０００７】
ラジアルすきまの狭小化の実現のため、各部品寸法の公差狭小化を図っているが、スパイダ２３を除いて、ヨーク２０および針状ころ軸受３０の外輪３１はプレス成形品であるため、自ずから限度がある。
【０００８】
そこで、従来は、ヨーク２０の軸受孔２２に対するシエル形針状ころ軸受３０の圧入後、その針状ころ軸受３０に適した外径をもつトラニオン２４を選択して組み合わせるようにしている。
【０００９】
【発明が解決しようとする課題】
ところで、上記のように、圧入後の針状ころ軸受３０に対してトラニオン２４を選択組合わせする自在継手においては、組立てに非常に手間がかかる問題がある。
【００１０】
この発明の課題は、ラジアルすきまをなくすことができるようにした自在継手用シエル形針状ころ軸受を提供することである。
【００１１】
【課題を解決するための手段】
上記の課題を解決するために、この発明においては、ヨークの二股片に形成された軸受孔に嵌合する円筒部の一端に底を設けた金属薄板のプレス成形品からなる外輪と、上記円筒部の内周軌道面に沿って転動自在に設けられた複数の針状ころとから成る自在継手用シエル形針状ころ軸受において、前記円筒部を、前記軸受孔の半径より曲率半径が大きく、軸受孔内に対する組み込み状態で両端部が軸受孔の内周に圧接するとともに、その圧接部間において軸受孔の内周との間に微小隙間を形成する周方向の長さが略等しい３つ以上の円弧状壁部により形成した構成を採用している。
【００１２】
上記のように、円筒部を軸受孔の半径より曲率半径が大きい３つ以上の円弧状壁部で形成すると、シエル形針状ころ軸受内にスパイダのトラニオンを挿入して、そのトラニオンを回転自在に支持した場合に、研磨仕上げされた真円度の高い上記トラニオンにより円弧状壁部の周方向の２等分位置が針状ころを介して押圧されて外方向に弾性変形し、その復元弾性によって針状ころがトラニオンの外周に圧接されることになり、シエル形針状ころ軸受とトラニオン間のラジアルすきまをなくすことができる。
【００１３】
ここで、３つ以上の円弧状壁部は、外輪の軸方向幅の全体にわたって形成されたものであってもよく、あるいは上記軸方向幅の一部分に形成されたものであってもよい。円弧状壁部の幅を軸方向幅の一部分とする場合、幅寸法が小さ過ぎると針状ころの安定性が悪くなるため、外輪軸方向幅の１／３以上の幅で上記円弧状壁部を形成する。
【００１４】
また、軸受孔に対して外輪を安定よく取付けるため、円弧状壁部の個数は３つ以上とするのが好ましい。
【００１５】
自在継手において、現実に問題となっているシエル形針状ころ軸受のラジアルすきまは５〜６μｍ程度であるため、前記円筒部の外径の真円度を３μｍ以上とすることにより、前記ラジアルすきまを完全になくすことができる。
【００１６】
【発明の実施の形態】
以下、この発明の実施の形態を図１および図２に基づいて説明する。図示のように、シエル形針状ころ軸受Ａは、外輪１と、その外輪１内に組込まれた複数の針状ころ１０とから成る。
【００１７】
外輪１は金属薄板のプレス成形品から成る。この外輪１は円筒部２の一端に底３を設けている。針状ころ１０は円筒部２の内周の軌道面４に沿って転動自在とされ、上記円筒部２の他端に設けた鍔５によって抜け止めされている。
【００１８】
外輪１の円筒部２は周方向の長さが略等しい３つの円弧状壁部２ａで形成されている。
【００１９】
ここで、シエル形針状ころ軸受によってトラニオンを回転自在に支持した自在継手において、現実に問題とされるラジアルすきまは５〜６μｍ程度であるため、外輪１の円筒部２の真円度を３μｍ以上としている。
【００２０】
上記の構成から成るシエル形針状ころ軸受Ａは、図３に示すヨーク２０の二股片２１に形成された軸受孔２２に外輪１の円筒部２を圧入し、円周方向に並ぶ針状ころ１０内にトラニオン２４を挿入して、このトラニオン２４を回転自在に支持する。
【００２１】
ここで、軸受孔２２に対する円筒部２の圧入時、その円筒部２を形成する円弧状壁部２ａの連接部２ｂが軸受孔２２の内周に圧接し、上記円弧状壁部２ａの周方向長さの２等分位置においては軸受孔２２の内周との間に微小の隙間が形成され、あるいはその内周に対して軽く接触している。
【００２２】
また、軸受孔２２に取付けられたシエル形針状ころ軸受Ａの針状ころ１０内にトラニオン２４が挿入された状態で円筒部２の３つの円弧状壁部２ａは、その周方向の２等分位置が針状ころ１０を介して押圧されて図２の鎖線で示すように外径方向に弾性変形し、その変形による復元弾性によって針状ころ１０はトラニオン２４の外周に押し付けられる。このため、シエル形針状ころ軸受とトラニオン２４間におけるラジアルすきまが形成されるという不都合の発生はなく、図３に示す２つのヨーク２０間において回転トルクを円滑に伝達することができる。
【００２３】
また、円弧状部２ａの数を３つとしたことにより、シエル形針状ころ軸受は、１２０°の間隔をおいてトラニオン２４と３点で強く弾性接触するため、トラニオン２４をきわめて安定よく支持することができる。
【００２４】
ここで、円弧状壁２ａの幅寸法が外輪１の軸方向幅の１／３未満であると、針状ころ１０の落ちつきが悪いため、図１に示すように上記幅寸法Ｌ1 は、外輪開口端から外輪軸方向幅Ｌ0 の１／３以上の幅寸法としておくようにする。
【００２５】
【発明の効果】
以上のように、この発明においては、シエル形針状ころ軸受内にトラニオンを挿入すると、円弧状壁が外径方向に弾性変形し、その復元弾性によって針状ころがトラニオンの外周に圧接されるため、シエル形針状ころ軸受とトラニオン間のラジアルすきまをなくすことができ、自在継手の２つのヨーク間において円滑に回転トルクを伝達することができる。
【図面の簡単な説明】
【図１】この発明に係るシエル形針状ころ軸受の縦断正面図
【図２】同上の横断平面図
【図３】（Ｉ）は従来のシエル形針状ころ軸受を用いた自在継手の縦断正面図、（II）は（Ｉ）のａ−ａ線に沿った断面図
【符号の説明】
１ 外輪
２ 円筒部
２ａ 円弧状壁部
１０ 針状ころ[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a needle roller bearing incorporated in a universal joint.
[0002]
[Prior art]
In an automobile steering device that steers a wheel by rotating the steering wheel, a steering shaft that transmits the rotation of the steering wheel to the steering gear box is formed by two relatively angled shafts, and the two shafts are connected by a universal joint. Thus, there is known one that transmits rotational torque between two axes.
[0003]
3 (I) and 3 (II) show an example of a universal joint used in the steering device. In this universal joint, a bearing hole 22 is formed in a bifurcated piece 21 provided in each of a pair of yokes 20, trunnions 24 provided in spiders 23 are inserted into the bearing holes 22, and each trunnion 24 is inserted into the bearing hole 22. It is rotatably supported by a shell-type needle roller bearing 30 press-fitted into the shaft.
[0004]
Here, the shell-type needle roller bearing 30 is rolled along an outer ring 31 having a bottom 31b at one end of a cylindrical portion 31a press-fitted into the bearing hole 22 and a raceway surface 32 on the inner periphery of the cylindrical portion 31a. The outer ring 31 is a press-formed product made of a thin metal plate.
[0005]
In the universal joint configured as described above, if there is a radial clearance Δr between the trunnion 24 of the spider 23 and the needle roller bearing 30, there is a backlash corresponding to the radial clearance between the connecting portions of the pair of yokes 20. As a result, the rotational torque cannot be smoothly transmitted between the two shafts connected to each yoke 20.
[0006]
For this reason, in the steering device, in order to improve the rotational operability of the steering wheel, there is a demand for narrowing the radial clearance between the needle roller bearing and the trunnion.
[0007]
In order to reduce the radial clearance, the tolerances of the dimensions of each part are reduced. However, except for the spider 23, the yoke 20 and the outer ring 31 of the needle roller bearing 30 are press-formed products. There is.
[0008]
Therefore, conventionally, after the shell-type needle roller bearing 30 is press-fitted into the bearing hole 22 of the yoke 20, a trunnion 24 having an outer diameter suitable for the needle roller bearing 30 is selected and combined.
[0009]
[Problems to be solved by the invention]
By the way, as described above, in the universal joint in which the trunnion 24 is selectively combined with the needle roller bearing 30 after press-fitting, there is a problem that it takes much time to assemble.
[0010]
An object of the present invention is to provide a shell-type needle roller bearing for a universal joint that can eliminate a radial clearance.
[0011]
[Means for Solving the Problems]
In order to solve the above problems, in the present invention, an outer ring made of a press-formed product of a thin metal plate provided with a bottom at one end of a cylindrical portion that fits into a bearing hole formed in a bifurcated piece of a yoke, and the cylinder In a shell-type needle roller bearing for a universal joint composed of a plurality of needle rollers provided so as to be able to roll along the inner circumferential raceway surface, the cylindrical portion has a radius of curvature larger than the radius of the bearing hole. In the assembled state with respect to the inside of the bearing hole, both end portions are in pressure contact with the inner periphery of the bearing hole, and a circumferential gap is formed between the press contact portions with the inner periphery of the bearing hole. The configuration formed by the above arc-shaped wall is employed.
[0012]
As described above, when the cylindrical part is formed by three or more arc-shaped wall parts having a radius of curvature larger than the radius of the bearing hole , a spider trunnion is inserted into the shell type needle roller bearing, and the trunnion is freely rotatable. , The circumferentially bisecting position of the arc-shaped wall portion is pressed through the needle rollers by the polished trunnion having a high roundness, and elastically deforms outwardly, thereby restoring its elasticity. As a result, the needle roller is pressed against the outer periphery of the trunnion, and the radial clearance between the shell needle roller bearing and the trunnion can be eliminated.
[0013]
Here, the three or more arc-shaped wall portions may be formed over the entire axial width of the outer ring, or may be formed in a part of the axial width. When the width of the arc-shaped wall portion is a part of the axial width, since the stability of the needle roller is deteriorated if the width dimension is too small, the above-mentioned arc-shaped wall portion has a width of 1/3 or more of the outer ring axial width. Form.
[0014]
Further, in order to stably attach the outer ring to the bearing hole, the number of arcuate wall portions is preferably three or more.
[0015]
In a universal joint, the radial clearance of a shell needle roller bearing that is a problem in reality is about 5 to 6 μm. Therefore, by setting the roundness of the outer diameter of the cylindrical portion to 3 μm or more, the radial clearance is increased. Can be completely eliminated.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to FIGS. As shown in the figure, the shell type needle roller bearing A includes an outer ring 1 and a plurality of needle rollers 10 incorporated in the outer ring 1.
[0017]
The outer ring 1 is made of a metal thin plate press-formed product. The outer ring 1 has a bottom 3 at one end of a cylindrical portion 2. The needle roller 10 is allowed to roll along the inner raceway surface 4 of the cylindrical portion 2, and is prevented from coming off by a flange 5 provided at the other end of the cylindrical portion 2.
[0018]
The cylindrical portion 2 of the outer ring 1 is formed by three arcuate wall portions 2a having substantially the same length in the circumferential direction.
[0019]
Here, in the universal joint in which the trunnion is rotatably supported by the shell-type needle roller bearing, the radial clearance, which is actually a problem, is about 5 to 6 μm, so the roundness of the cylindrical portion 2 of the outer ring 1 is 3 μm. That's it.
[0020]
In the shell-type needle roller bearing A having the above-described configuration, the cylindrical portion 2 of the outer ring 1 is press-fitted into the bearing hole 22 formed in the bifurcated piece 21 of the yoke 20 shown in FIG. A trunnion 24 is inserted into 10 and the trunnion 24 is rotatably supported.
[0021]
Here, when the cylindrical portion 2 is press-fitted into the bearing hole 22, the connecting portion 2b of the arc-shaped wall portion 2a forming the cylindrical portion 2 is pressed against the inner periphery of the bearing hole 22, and the circumferential direction of the arc-shaped wall portion 2a. A minute gap is formed between the inner circumference of the bearing hole 22 at a position that bisects the length, or light contact with the inner circumference.
[0022]
In addition, the three arcuate wall portions 2a of the cylindrical portion 2 in the state in which the trunnion 24 is inserted into the needle roller 10 of the shell needle roller bearing A attached to the bearing hole 22 are two in the circumferential direction. The minute position is pressed through the needle rollers 10 and elastically deforms in the outer diameter direction as shown by the chain line in FIG. 2, and the needle rollers 10 are pressed against the outer periphery of the trunnion 24 by the restoring elasticity due to the deformation. Therefore, there is no inconvenience that a radial clearance is formed between the shell needle roller bearing and the trunnion 24, and the rotational torque can be smoothly transmitted between the two yokes 20 shown in FIG.
[0023]
Further, since the number of the arc-shaped portions 2a is three, the shell-type needle roller bearing strongly elastically contacts the trunnion 24 at three points with an interval of 120 °, so that the trunnion 24 is supported extremely stably. be able to.
[0024]
Here, when the width of the arcuate wall 2a is less than 1/3 of the axial width of the outer ring 1, for calm the needle roller 10 is poor, the width dimension L 1 as shown in FIG. 1, the outer ring The width dimension is set to be 1/3 or more of the outer ring axial direction width L 0 from the opening end.
[0025]
【The invention's effect】
As described above, in the present invention, when the trunnion is inserted into the shell type needle roller bearing, the arc-shaped wall is elastically deformed in the outer diameter direction, and the needle roller is pressed against the outer periphery of the trunnion by its restoring elasticity. Therefore, the radial clearance between the shell type needle roller bearing and the trunnion can be eliminated, and the rotational torque can be smoothly transmitted between the two yokes of the universal joint.
[Brief description of the drawings]
FIG. 1 is a longitudinal front view of a shell type needle roller bearing according to the present invention. FIG. 2 is a cross-sectional plan view of the same. FIG. 3 (I) is a longitudinal view of a universal joint using a conventional shell type needle roller bearing. Front view, (II) is a cross-sectional view along line aa in (I).
DESCRIPTION OF SYMBOLS 1 Outer ring 2 Cylindrical part 2a Arc-shaped wall part 10 Needle roller

Claims (2)

ヨークの二股片に形成された円形の軸受孔に嵌合する円筒部の一端に底を設けた金属薄板のプレス成形品からなる外輪と、上記円筒部の内周軌道面に沿って転動自在に設けられた複数の針状ころとから成る自在継手用シエル形針状ころ軸受において、前記円筒部を、前記軸受孔の半径より曲率半径が大きく、軸受孔内に対する組み込み状態で両端部が軸受孔の内周に圧接するとともに、その圧接部間において軸受孔の内周との間に微小隙間を形成する周方向の長さが略等しい３つ以上の円弧状壁部により形成し、各円弧状壁部を、外輪の開口端から外輪軸方向幅の１／３以上の幅で形成したことを特徴とするステアリング用の自在継手用シエル形針状ころ軸受。An outer ring made of a metal sheet press-molded product having a bottom at one end of a cylindrical portion that fits into a circular bearing hole formed in a bifurcated piece of the yoke, and freely rollable along the inner circumferential raceway surface of the cylindrical portion In a shell-type needle roller bearing for a universal joint comprising a plurality of needle rollers provided on the bearing, the cylindrical portion has a radius of curvature larger than the radius of the bearing hole, and both ends are bearings in an assembled state in the bearing hole. Each circle is formed by three or more arc-shaped wall portions that are in pressure contact with the inner periphery of the hole and that form a minute gap between the press contact portions and the inner periphery of the bearing hole. A shell-type needle roller bearing for a universal joint for steering, wherein the arc-shaped wall portion is formed with a width of 1/3 or more of the width in the outer ring axial direction from the opening end of the outer ring. 前記円筒部の外径の真円度が３μｍ以上であることを特徴とする請求項１に記載のステアリング用の自在継手用シエル形針状ころ軸受。 The shell-type needle roller bearing for a universal joint for steering according to claim 1, wherein the roundness of the outer diameter of the cylindrical portion is 3 µm or more .
JP34638598A 1998-12-07 1998-12-07 Shell-type needle roller bearings for universal joints for steering Expired - Fee Related JP3919366B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP34638598A JP3919366B2 (en) 1998-12-07 1998-12-07 Shell-type needle roller bearings for universal joints for steering
DE19958059A DE19958059A1 (en) 1998-12-07 1999-12-02 Shell-type needle roller bearing for universal joint has cylinder formed by curved sections, preventing formation of radial gaps
US09/453,212 US6334714B1 (en) 1998-12-07 1999-12-03 Needle roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP34638598A JP3919366B2 (en) 1998-12-07 1998-12-07 Shell-type needle roller bearings for universal joints for steering

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JP2000170755A JP2000170755A (en) 2000-06-20
JP3919366B2 true JP3919366B2 (en) 2007-05-23

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DE10337581A1 (en) * 2003-08-16 2005-03-10 Zahnradfabrik Friedrichshafen Planet drive, comprising elliptical axle surrounded by ball bearing with circular inner path
JP4508588B2 (en) * 2003-09-16 2010-07-21 Ｎｔｎ株式会社 Shell needle roller bearing
JP4508587B2 (en) * 2003-09-16 2010-07-21 Ｎｔｎ株式会社 Shell needle roller bearing
JP2005105856A (en) * 2003-09-29 2005-04-21 Ntn Corp Piston pump driving part supporting structure
JP4508591B2 (en) * 2003-09-24 2010-07-21 Ｎｔｎ株式会社 Compressor spindle support structure
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US8033738B2 (en) * 2006-11-09 2011-10-11 Nexteer (Beijing) Technology Co., Ltd. Needle roller bearing
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